Lens grinding and polishing machine



March 5, 1940.-.. Y w, A, LOCKHART l 1 2,192,486 v I LENS GxIND-ING ANDPOLISH'ING MACHINE Filed sept. 1, 1937 Ve 'sheets-sheet 1 V l /4 1*|l\o`s [38 As' A mgm - ATrnRnEY w.I A. LocYKHAR-r l l2,192,486 LENSlGRINDING AND PLIsHING MACHINE Maurch 5, 1940.

Filed Sept. l, 1937 l 6 Sheets-Sheet 4 mi( @M ATT URNEY March 5, 1940.w, AQ LOCKHART LENS GRINDING AND POLISHING MACHINE Filed Sept. l1, 19576 Sheets-Sheet 5 l ATTEIHHEY March 5,-1940. w. A. LocKHAR-r LENSGRINDINGAND POLISHING MACHINE Filed Sept. 1, 1957 6 Sheets-Sheet 6lNvl-:NT DR Jmf @www ATTDRNEY Patented Mar. 5, v11940 Y y lauren` STATESLENS GRINDING AND POLISHING MACHINE William A. Lockhart, Waterloo, N.Y., assigner tc Shuron Optical Company, Inc., Geneva, N. Y., acorporation of New York Application September 1, 1937, Serial No.161,985

14 Claims.

This invention relates to improvements in a -surface or lens grindingand polishing machine, in which a plurality of (in this instance two)grinding and polishing couples. each consisting of a lens holder andgrinding lap, are operated in synchronism by a combination of tworeciprocative movements and two variations or break-up movements. Thetwo reciprocative movements operate in different directions, preferablyat'right angles to each other, and the two continuous variation orbreak-up movements operate in conjunction with the reciprocativemovements; whereby the paths of travel of the movable elements of thegrinding and polishing couples are changed during successive strokes sothat each lens will be moved relative to the grinding surface of thecouple through a series of curvilinear strokes to thereby producesurfaces which are free from deformations and waves. This invention isan improvement on the structure shown in Patent No. 1,709,943, issued toE. M. Long, April 23, 1929, and also on my co-pending application, nowPatent No. 2,168,343, issued- August 8, 1939.

An object of this invention is to provide a machine, which is ofimproved simplified construction, for grinding and polishing thesurfaces of lenses or analogous objects; that is, a machine ywherein thevarious movable parts thereof will operate more eiiicaciously thanheretofore, and thereby more Vexpeditiously and accurately grind orpolish such surfaces to the desired contour and nish.

A more specific object of the invention is to provide a grinding andpolishing machine of the above mentioned class with improved mechanismsassociated with the two major ,or reciprocative movements for producinga break-up in the strokes thereof whereby the path of transversing A0movement of the movable elements of each grinding and polishing couplewill be caused to vary throughout successive strokes of a cycle ofoperation, and particularly to produce alterations in the positions ofreversal at the ends of successive strokes of the relative movement ofthe lens, or other object, and the grinding surface or lap, and therebyto greatly increase the duration of each cycle of operation or theperiod between r the operation of the lens, or other object,a secondtime through a given path; so that the lens or object will not be movedtwice through the same path or a portion thereof during the timeordinarily required to grind or polish a surface there- 5 of, andtherefore any minutev inaccuracies 0ccurring in the surface of the lapwill not be reproduced on the surface being ground.

`Other specic objects of the invention are: First, to provide aconnecting rod associated with one of the major or reciprocativemovements of 5 the grinding and polishing couples which is of improved,simplified construction and which is arranged to operate in an improved,more direct manner than the corresponding connecting .rod shown in theabove mentioned patent; second, 10 to provide an improved structureconnecting the main drive element or shaft with the reciprocatingmembers or rock frame 3, associated with the two reciprocative movementsto break up or alter the normall movements thereof, so that a slow, 15continuous change in the path of the relative Y movement of a lens andthe grinding orpolishing surface, and particularly in the reversingpoints thereof throughout successive strokes of the cycle of operationover an extendedbr indefinite period 20 and thus eliminate the formationof lines, waves or other defects in the lens surface which may cause azone or aberration; third, to provide the drive mechanism with a simplyconstructed clutch means whereby the movable elements of the 25grindingp and polishing couples may be selectively operated at either oftwo speeds,-a relatively slow speed for wax polishing and when grindinghigh or complex curved surfaces, or a relatively high speed for'grindingsurfaces of relatively low 30 pitcher curves, -depending upon theoperation -to be performed; fourth, to provide a removable rouge feedwhereby the same may be used only when a surface is being polished; fth,to provide the drive elements or arms for transmitting mo- 35 tion fromthe reciprocating members or rock frames to the work or lens holderswhich are of improved structure. In' carrying out this object, the drivearms or elements are so constructed that the weight thereof is arrangedas close to 40 the axis of movement or rotation of the elements aspossible, whereby saidv elements will operate with a minimum amount ofvibration and power and the pressure between the works and grinding lapor surface will be maintained more nearly '45 uniform, particularly atthe point of reversal of the drive elements or arms at the end of onestroke and the beginning of the next stroke; sixth,

Ato provide an improved selective tension means whereby the work may bereadily. moved into and maintained in operative relation with thegrindingand polishing surface under a predetermined pressure, that is, apressure most advantageous'to the form or type of the worksurface beingground.

or polished; seventh, to so construct this machine that the variousmoving parts thereof will be adequately lubricated for an extended orindciinite period so that the machine will successfully operate withouta continuous iiow of lubricating iiuid to the various bearing membersthereof and the mechanism for producing such iiow.

Other objects and advantages relating to the speciiic construction ofthe parts of the machine will more fully appear from the followingdescription taken in conjunction with the accompanying drawings inwhich:

Figure 1-is a front elevation of a lens grinding and polishing machineembodying the various features of thisinvention.

Figure 2 is a top plan, partly broken away and in sections, of themachine shown in Figure 1 witlthe top removed to illustrate the interiorconstruction.

Figure 3 is a detail longitudinal vertical sectional view takensubstantially on line 3 3, Figure 2.

Figure 4 is a detail vertical sectional view taken on line 4 1, Figure3.

Figure 5 is a detail horizontal sectional view taken substantially online 5 5, Figure 3, illustrating the greater portion of the gear case orhousing and the bearing bracket in elevation.

Figure 6 is a detail horizontal sectional view on an enlarged scale,taken substantially online 6 6, Figure 3.

Figure '7 is a vertical sectional View taken on line 1 1, Figure 3.

Figure 8 is a longitudinal vertical sectional view taken on line 8 8,Figure 2.

Figure 9 is a detail vertical sectional view taken substantially inv theplane of the line 9 9, Figure 8, anouter end portion of the lens drivingmember or arm and the lens holder connected thereto being broken away.

Figure 10 is a longitudinal vertical sectional view, partly inelevation, taken substantially in the plane of the line I Il I Il,Figure 2.

Figure 11 is a detail sectional view taken on line II II, Figure 10.

Figure 12 is a detail horizontal sectional View taken on line I 2 I 2,Figure 10.

Figure i3 is a detail vertical sectional view of the upper portion ofthe supporting frame illustrating my novel mechanism for producing apredetermined pressure between the lens and the grinding surface or lap.in side elevation, as

viewed from line I3 I3. Figure l.

Figure 14 is a detail vertical sectional view through the pressureproducing mechanism taken substantially on line I 4 I4. Figure l.

Figure 15 is a horizontal sectional view taken substantially on line I5I5, Figure 13.

Figure 16 is a detail vertical sectional view of the upper end portionof the rn'essurev producing mechanism shown in Figure i3 takensubstantially on line I6 I6. Figure 15.

Figure 17 is a horizontal sectional view through the guide post andsleeve taken substantially on line I1 I1. Figure 13.

Figure 18 is a sectional view taken on line I8 I8, Figure 6.

Figures 19 to 22 inclusive are diagrammatic views illustrating theoperation of my novel motion break-up mechanism associated with thereciprocative movement operating substantially parallel with the baseaxis nf the lens.

Figure 23 is a.` diagrammatic plan View of one of the lens holder driveelements illustrating the reciprocative movement thereof operatingsubstantially parallel with the cylinder axis of the lens being groundand which is usually called the cross stroke.

Figure24isavlewsimilartoFlgm-e23 illustrating the reclprocative movementof a lens holding drive element operating substantially parallel withthe`base axis of the lens being ground and which is usually called thelengthwise stroke.

Figure 25 is a diagrammaticview illustrating the action of the driveelement upon the lens holder when' grinding or polishing a convexsurface.

Figure 26 is a view similar to Figure 25 illustrating the action of thedrive element upon the lens holder when grinding a concave surface.

Figure 27 is a diagrammatic view illustrating succeeding strokes of alens over the grinding surface of a lap produced either by the crossstroke or the lengthwise stroke of the drive element.

Figures 28, 29, 30 and 31 are diagrammatic views illustrating the pathof travel of a given point on the lens, for instance the center, overthe grinding surface of the lap, each gure showing the movement of thelens through ten consecutive revolutions of the drive shaft.

I'he construction illustrated in the drawings comprises a mainsupporting frame I consisting of a substantially rectangular housingsection 2 and a top section or cover 3 removably secured to the housing2 by any suitable means. I'he housing 2 in this instance has the lowerside thereof open and is provided with a pair of ribs 4 extendingtransversely therethrough adjacent the bottom or lower edge in spacedrelation to each other. The top section 3 may, as indicate in Figures 1and 3, have an opening 3' in the upper side thereof which is closed by alid 5. A main drive shaft 6 is journaled in suitable bearings l and I torevolve about a horizontal axis. The bearing 'I is mounted in one of theend walls of the housing section 2, while the bearing 1I is mounted in abracket 8 secured to the rear side wall of said housing intermediate theends thereof. One end of the shaft 6 extends some distance outwardlybeyond the adjacent end wall of the housing 2 and has secured thereto ahand wheel 9 by which the shaft may be manually rotated.

Mounted upon the shaft 6 intermediate the hand wheel 9 and housing 2 isa simple drive mechanism adapted to be connected with any suitablesource of power, not shown, as by a belt I 0 whereby the shaft may berotated at either of two speeds. This drive mechanism comprises a pairof grooved pulleys II and I2 mounted upon the shaft 6 in axial spacedrelation to each other and a pair of fiat faced pulleys I3 and I4positioned intermediate the pulleys IIJ and II. The grooved pulley II isfixed to the shaft 6 by any suitable means, as a pin I5. while the othergrooved pulley I2 is loosely mounted on said shaft to rotate relativelythereto. The pulleys II and I2 are connected by belts I 6 andkI'I tosimilar pulleys I8 and I9 rotatably mounted upon a shaft 20 secured tothe housing 2 in front of the shaft 6. pulleys I8 and I9 being connectedto each other. as shown in Figure 2. to rotate in unison. The pulley IIis preferably of greater diameter than the pulley I2, while the pulleyI8. connected by the belt IB to pulley I I is of smaller diameter thanthe pulley I9 which is connected by belt II to pulley I2, as clearlyillustrated in Fig-ure 2. The pulleys I3 and I4, which are adapted to beoperated by the belt I0 are loosely mounted upon the shaft Il to rotaterelative thereto. The pulley I4 is an idler pulley and, as shown, ismounted upon a roller bearing 2| mounted upon the hub portions l2' andI3' of pulleys I2 and I3 respectively.

The pulley I3 is adapted to be connected with either pulley II or I2 bya simple clutch mechanism which, as shown, consists of clutch pins 22mounted in the hub portions II' and I2' of pulleys I I and I2respectively and a clutch pin 23 mounted in the hub portion I3' of thepulley I3. The clutch pins 22 are flxedly secured to the respective hubportions II' and I2' to extend inwardly toward each other beyond theadjacent surfaces Aof said hub portions into corresponding -recesses 24provided between the pulleys I3 and pulleys II. and I2, as shown inFigure 3. The clutch pin 23 is slidably mounted in thehub portion I3' ofpulley I3 for movement into and out of engagement with the pins 22.'I'he clutch pin 23 is moved axially relative to the pulley I3 by a camrod 25 which extends inwardly from the outer face of the pulley I3through a suitable hole provided in the pulley and has the inner endthereof provided with an eccentric portion or extension 25' received ina suitable aperture provided in the pin 23 intermediate the endsthereof. The cam rod 25 is maintained against outward axial movementbya, pin 26 which extends diametrically through the rod adjacent the outerwall of a slot 21 formed in thev web portion of the pulley I3.

It will now be observed thatv when the belt I 0 is shifted from the idlepulley I4 onto the drive pulley I3, motion from the pulley I3-may betransmitted either directly tothe'pulley II and shaft 6 through themedium of clutch pin 23 and one of the clutch pins 22 connected withpulley II so that the shaft 6 will be operated at the same speed as thepulley I3. If, on the other hand, it is desired to operate the shaft ata slower rate of speed than that of the pulley I3, the clutch pin 23 maybe moved by rotating the cam rod 25 out of engagement with the clutchvpins 22 associated with the pulley II into operative engagement withclutchv pins 22 associated with the pulley I2. Rotation of the pulley I3will now transmit motion through the pulley I2 and belt I1 to pulleys I9and I8 and then through belt I6 to pulley II and shaft 6.

The shaft 6 is adapted to operate the movable elements of the two lenssurface grinding and polishing couples which comprise a grinding lap 28mounted `on a relatively stationary lap supporting element 29 and-a workor lens supporting block 30 operatively connected to a lens drivingelement for moving the work or lens as L, Figures 10, 13, 14, across andupon the upper surface of a lap 28. The laps 28 are of course of variouscontours and must be interchanged from time to time upon the supportingelement 29. For this reason each lap is releasably held in operativeposition on a support 29 by a plate 33 arranged at the front side of asupporting block 34 and a second plate 35 positioned at the rear side ofsaid block, as illustrated in Figure 9, said plates being clamped to thesupporting block by a screw 36. The blocks 34 are each provided with apendant hollow hub 34' which is adapted to removably receive the upperend portion of a bolt 31 mounted on a, boss 38 provided in the bottomwall 38 of a catch basin 39, see Figure 10.

`The supporting -elements 29 are removably mounted on the bolts 31, andin order that these elements may be releasably maintained in operativeposition, the upper end portion of each bolt l 31 isprovided with'a pin40 which is adapted to be received in an elongated slot 4I extendingupwardly from the lower end of each -hub portion -34' as shown in Figure10. The supporting elements 23 are constructed with hubs 34' of dif--ferent lengths so as to adapt them for maintaining the grinding lap 28at different elevations with respect to the driving elements 31,50 as toadapt is a relatively long member, as illustrated at the left hand sideof Figure 10. If,on the other hand, a minus or concave lens is beingground or polished, the same is maintained at a relatively low level andthe hub 34 is a relatively short member, as illustrated at the righthand side of Figure 10. Also, if a substantially fiat lens is to beground or polished, the lap 28 will be maintained at an intermediateposition and the hub 34 will be of intermediate length.

The catch basin 39 is removably secured to the housing 2 by a pair ofbolts 43 extending through corresponding holes or apertures at oppositeends of the catch basin 33, and are screwthreaded in the front wall ofthe housing 2. Each of these bolts 43, as shown more particularly inFigure 11, are of substantially uniform diameter throughout the lengththereof, and is provided with an annular recess or groove, 43 in theperiphery thereof a short distance from the outerl end, A slotted washer44 extends into the groove 43' for maintaining the catch basin againstoutward 4movement axially from the screws `43. The washers 44 areclamped in the grooves 43' when the screws 43 are tightly screw-threadedin the housing 2; and when it is desired-to remove the catch basin, itis only necessary to rotate the screws 43 to move them axially outwardlya short distance relatively to the housing 2 to release the washers 44.Then by removing the washers from their respective grooves 43', thecatch basinl may be drawn outwardly over the screws and thus removedfrom the housing 2. Likewise, the catch basin may be readily mounted onthe housing 2 by sliding them onto the screws 43, inserting the washers44 in the grooves 43' and then tightening the screws. I

Lens drive element The lens driving elements 3| are of novelconstruction and, as shown in Figures 2 and 14, each comprises a spindle46 journaled in suitable ball bearings 41 mounted in theouter endportions 48 of a D-shaped -frame 49 which is rotatably supported by stubshafts or studs 50 carried by a. substantially horizontally disposedfloating member or beam 5| mounted in the housing 2 in front of shaft 6.Each spindle 46 extends outwardly from the interior of the housing 2through an opening 52 provided in -the front wall of the housing 2 andhas connected to the outer end thereof a drive frame 53 for the lensholder or supporting block 3l. Each drive frame 53 compr'ses asubstantially U-shaped-bracket 54 and a saddle memberI 55. The bracketmember 54 has the center thereof provided with a hollow hub 54 which isadapted to removably receive the outer end of the spindle 46 therein.The bracket 54 is secured to the spindle 46 by means of a pin 56 whichextends through the hub 54 and said spindle. The outer ends of 'the arms54" of the bracket 54 are provided with hardened bearings 51 adapted tobe engaged' by pointed pins 58 mounted on the opposite ends of thesaddle member 55 which, in turn, is adapted to receive a supportinglens'block holder 59 which is secured to the central portion of thesaddle 55 by a screw 60, as shown in Figures 2 and 14.

The lens block holder 59 comprises a body portion 6| provided with ashoulder 6| at the lower, inner or rear edge thereof. A clamp plate 62is secured by a screw 63 to the outer face of the body portion 6| forfirmly clamping the rib 64 of the lens holder 30 between the lower edgethereof and the shoulder 6 I The bearing members 51 are tightly securedin the opposite ends of the bracket member 54 and are provided withconical sockets in their lower faces for receiving the upper taperedends of the pins 58 which engage the sockets in about the horizontalplane of the axis of rotation of the corresponding spindle 46, asillustrated in Figures 10 and 13. As shown in Figure l0, the centralportion of each saddle member 55 extends across and some distance abovethe upper surface of the lap 28 and with the opposite side portions 55"of the saddle extending downwardly in diverging planes to a positionbelow the adjacent ends of the bracket 54 to support the bearing pins 58and to allow free lateral rocking movement of the saddle and its lensblock holder 59 without liability of contact with the lap or itssupporting means.

In order that lenses of various curvatures, whether concave or convex,may move across the surface of the lap 28 with a minimum. amount ofpower and with a substantially uniform pressure maintained between thelens and the grinding surface of the lap, the side portions 55 may varymaterially in length in different saddle members 55. The reason for thisis to maintain the lens at one or the other side of the horizontal planepassing through the axis of rotation of the spindle 46, depending uponthe curvature of the surface being ground. That is, when the surface tobe ground is of convex curvature, the side portions 55' are ofrelatively long length so as to hold the lens above the horizontal planepassing through the axis of rotation of the spindle 46, as shown at theleft hand side of Figure 10.

On the other hand, if the surface to be ground is of concave form, thenthe side portions 55 of the saddle are of relatively short length so asto maintain the lens, and particularly the surface thereof to be ground,below the horizontal plane passing through said spindle 46, asillustrated at the right hand side of Figure 10. Again, if the surfaceof the lens, or other object to be ground, is substantially fiat theside portions 55 of the saddle are of medium length so as to maintainsaid surface to be ground in substantially a horizontal plane passingthrough the axis of rotation of the spindle 46.

To explain more explicitly, the co-action of the various members of alens drive element 3i and the lap 28 when polishing lenses or otherobjects with surfaces of different curvatures, let it be assumed, first,that a plus or convex lens as illustrated at the left hand side ofFigure 10 and in Figure 25 is to be ground. This lens L is positioned,as shown, with the surface thereof to be ground above the axis X-X ofrotation of the spindle 46 by the selection of a saddle member 55 havingrelatively long side portions 55 and a lap support having Va relativelylong hub 34'.

It will now be apparent that inasmuch as the longitudinal thrust of thespindle 46 upon the lens holder 30 is applied at the points of contactof the pins 58 with bearings 51 below the connection of the lens withthe surface of the lap 26, the frictional resistance to the movement ofthe lens over the lap will tend to rotate the holder 30 and saddle 55 ina direction opposite to that of the movement of the spindle 46, asindicated by arrows N and N', Figure 25. The forward edge of the lenswill therefore tend to move away from the curved portion of the lapsurface coincident therewith at the beginning of each stroke of thedrive element 3|, so that the lens will tend to rock about the center ofcurvature of the grinding surface of the lap and thus prevent excessiveor uneven friction between the lap and lens.

If, on the other hand, a minus or concave lens is to beground, a saddle55 and lap support will be chosen having relatively short side portions55' and a relatively short hub 34' respectively, as illustrated on theright hand side of Figure 10 and in Figure 26 so as to position the lenssurface to be ground below the axis X--X of rotation of spindle 46 andtherefore below the point of contact of pins 58 with bearings 51. Inthis arrangement ofthe parts, the thrust of the spindle 46 during theaxial movement thereof upon the lens holder 30 will be applied-to saidholder'at the same side of said lens surface as the connection of thelens with the lens holder. It therefore follows that the force producedby the thrust of the lens upon the upwardly inclined central portion ofthe said lap at the beginning of each stroke will be applied to the lensholder radially outward from the surface of the lens contacting with thelap. This will tend to rock the lens holder forwardly or in thedirection of movement of the spindle'46 as indicated by arrows N and N',Figure 26 and thereby tend to rock the lens holder 20 and'the lenscarried thereby about the center of curvature of the lap surface or inthe direction of curvature of the grinding surface of the lap, so thatthe lens will move smoothly along said surface of the lap insubstantially coincidental contact therewith and therefore with aminimum amount of lateral thrust upon the surface of the lap,particularly at the beginning of each stroke.

`When a lens with a substantially at surface is to be ground, a saddlemember 55 and lap holderv 29 will be chosen which will maintain suchsurface of the lens substantially in the plane of the axis X-X ofrotation of the spindle 46. When the surface to be ground is in thisposition, the line of thrust of the spindle 46 during an axial movementthereof upon the lens holder is substantially coincident to the line ofthrust of lens upon the grinding surface of the lap so that the tendencyof the lens holder to be rotated upon the axis extending through thepoints of the pin 58 is reduced to a minimum, and the surface of thelens will be maintained in substantially coincidental contact with thegrinding surface of the lap.

It will therefore be seen that it will be necessary to frequently changethe saddle members in order to successfully grind surfaces of differentcurvatures, and this is readily accomplished due to the fact that thepins 58 have merely a bearing engagement with the bearings 51 so thatthe saddle members may be readily removed from the corresponding bracket54 by merely separating the bearing members 51 from the pins 58.

The term "coincidental contact is used in the specifications and claimsto designate that rela- Y gular relation with respect to each other.

The hereinbefore mentioned stub shafts 50 and 50' which rotatablysupport the-D frames 49 have the outer end portions and the centralportion thereof respectivelyv secured to the oat,

ing beam or member while the opposite end portions of the shaft 50 andthe outer end portions of the shaft 50' are each journaled in arespective roller bearing 66 secured in enlargedhousing portions 61formed ineach D framev49 at opposite endsv thereof. The stub shafts 50and 50' are arranged in cog-axial alignment with each other and with thecommon axis thereof intersecting the axes of rotation of the spindles46. It will therefore be understood that inasmuch as'the bracket members.54 are arranged substantially in a diametrical plane passing throughthe axis of the corresponding spindle 46 each lens driving element 3|will be in nearly a balanced condition and will therefore rotate with aminimum amount of power and vibration about the axis of the spindle 46as the lens is moved back and forth across 'the grinding surface of thelap.

Reciprocating rock frames or carriers The axial movement of spindle 4.6for moving the lens carried thereby through the cross strokes, that is,transversely of the grinding surface of a lap, and the lateral movementsof the spindle for producing the lengthwise strokes of the lenslongitudinally of the grinding surface of the lap are produced by theoperation of the floating beam 5| which has secured thereto a pair ofstuds or pivot shafts 69 extending'transversely of the beam intermediateshafts 50 and shaft 50', as illustrated in Figure 8. 'Ihe shafts 69 arearranged with the axes thereof intersecting the common axis of theshafts 50 and 50'. The shafts 69 have the ends thereof extendingoutwardly from the opposite sides of the beam 5| and journaled incorresponding` bearings 66 mounted in the upper end portions of a pairof supporting inverted V-frames 'l0 at opposite sides thereof andthrough which the beam 5l extends, as shown in Figures 8 and 9. 'I'heseframes 10 extend downwardly from the beam 5| to near the bottom of thehousing 2 and have securedto opposite sides of the lower ends thereof apair of stub shafts 1| arranged in co-axial alignment with each other.wardly from adjacent sides of the corresponding frame 10 and have theirends mounted in bear--l ings 66 secured in the opposite sides ofanoscillating frame 12 mounted in a vertical plane beneath the floatingbeam 5I and in spaced revlation thereto.

This oscillating frame 12 is provided with a pair of bearing members 66arranged in the ends thereof, as shown in Figure 8, and which receivethe respective ends of a pair of stub shafts 13 which are secured to thehereinbefore mentioned ribs 4 provided in the housing 2. The

shafts 13 are arranged in axial alignment with each other'with thecommon axis thereof intersecting the common axes of each pair of stub'shafts -`1|. It will therefore be obvious that the These shafts 1|extend inf frame'12, the beam 5| and the lens driving elements 8|connected thereto are free to rock about the common axis of the shafts13 extending longitudinally of the housing 2 in substantially parallelrelation with the minor or lateral axes of the laps 28. Furthermore, itwill be obvious that the `beam 5| and the lens driving elements 3lconnected thereto may reciprocate in a direction longitudinal of thehousing 2 and in substantially parallel relation with the major orlongitudinal axes of the laps 28, due to the rocking action of theframes 10 about theaxes of tht? shafts 1| extending transversely of thehousing 2. The mechanism for producing these rocking or oscillatingmovements of the frame 12 an beam 5| will now bedescribed.

. L engthwise reciprocating movement Mounted upon the drive shaft 6intermediate the bearings 1 and 1' is a spiral gear 15 which ispositioned within a gear housing or case 16 having bearings 11 arrangedin opposite ends thereof, as shown 'in Figure, for receiving the shaft 6therethrough and supporting a case 16 on said shaft. Thefcase 16 ismaintained against rotation during the rotation of shaft 6 by a pin 18secured in the hereinbefore mentioned bearing neath the shaft 6 and isjournaled in bearings 83 mounted in the case 16 to'rotate about an axisextending in right angular relation to the axis of rotation of shaft 6,as shown in Figure 4. Thev shaft 82 extends beyond the outer side of thecase 16 and has secured to the outer end thereof a grooved pulley 84which is connected by a belt 85 toa grooved pulley 86 secured to one endof a drive shaft 81 comprising a portion of one of my novel powertransmission and motion breakup mechanism 88.

This mechanism 88 comprises a case 89 which is secured to one end wallof the housing 2 as by screws 90 or their equivalent. The upper side ofthe case 89 is provided with a cover 89 removably secured thereto byscrews 9|, as indicated in` Figures 2 and 3. The case 89 is providedwith a pair of bearings 93 and 93' arranged in axial spaced relation toeach other in one side thereof, which rotatably supports the shaft 81,as shown in Figure 6, whereby said shaft may be rotated about a fixedaxis extending at substantially right angles to the axis of rotation ofthe drive shaft 6. The case 89 also has' a pair of axially spacedbearing members 94 mounted therein at one side of the bearings 93 and93' for rotatably supporting an eccentric sleeve 95 arranged-in parallelspaced relation to the shaft 81. A shaft 96 .is journaled in the sleeve95 to rotate about an axis arranged in spaced substantially parallelrelation with the-axis of rotation of said sleeve. The sleeve 95 hassecured to the one end thereof 'a gear 91 which is in meshing engagementwith a similar gear 98 splined or otherwise secured to the shaft 81 torotate in unison with said shaft. The

gears 91 and 98 are of the same pitch diameter so that the sleeve willbe rotated at the same rate of speed as the shaft 81.

The shaft 96 has one end thereof extending v forwardly beyond the case89 and supports an parallel with the axis of rotation of said shaft 96.'I'he crank pin 00 is held in different positions of angular adjustmentby means of a clamping screw engaged in a diametrically extendingthreaded aperture in the crank pin |00 and which extends outwardly fromthe crank pin through an elongated slot |02 provided in the adjacent endportion 96 of the shaft 96 which is enlarged to receive the pin 00therein. The crank pin |00 is provided with an eccentric extension |00which is arranged at one side of the axis of the crank pin.

Mounted upon the extension |00' is a ball bearing member |02 whichrotatably supports one end of my novel connecting rod |03. 'Ihis rod |03comprises a head |04 and a flexible shaft or rod |05. The head |04 isprovided with a bore |04 extending transversely therethrough for thereception of the bearing |02 and outer endportion of the crank pinextension |00'. The rod |05 is comprised of a flexible metal core |06which in this instance is in the form of a coil spring having one endthereof secured in a bore |04" provided in the head |04 in right angularrelation to the bore |04. The head |04 may, as shown in Figures 2, 6 and8, be slotted to form opposed sections at opposite sides of the bore|04" and which are provided with screws or bolts |01 whereby thesections may be clamped to the core |06 for securing the core to thehead 04. The core |06 is provided with a flexible cover |08 composed ofrubber, or the like, for providing the rod with a smooth outer surfaceand for maintaining the core free from dirt, grease or other foreignelements. from the head |04 to within a short distance of the oppositeend of the core which is clamped in a split hollow boss |09 by a screwH0, said boss being shown integral with the end of the floating beamopposite the transmission mechanism 88, as illustrated in Figures 2 and8.

The boss |09 is arranged, when the beam 5| `is substantially midwaybetween the extreme to an eccentric sleeve ends of the transverse strokethereof, in a plane extending substantiallyat right angles to the endportion |00 of thecrank pin 00 to which the connecting rod |03 isattached. It will, therefore, be seen that the connecting rod |03,during the rotation ofthe crank pin, will extend in substantially astraight line from the crank pin portion |00' to the boss |09 and willtherefore have substantially a direct thrust upon the oating beam 5|. Itwill also be observed by referring to Figure 8 that owing to theparticular construction of the beam 5| and rock frames 10 and 12 theconnecting rod |03 may freely extend between the floating beam and rockframe 12 and through the interior of the rock frame 1 0. It is,therefore,-evident that this structure is an improvement over thestructure shown in the hereinbefore mentioned Patent 1,709,943 whereinthe connecting rod corresponding to applicants -connecting rod |03 isnecessarily a more or less arcuate member to enable the same to extendaround the rock frames associated therewith.

The read end of shaft 96 extends a short distance beyond the sleeve 95and has secured thereto a gear member |2 which is ln meshing en-`Asagement with a similar gear member ||3 keyed ||4 which in turn is keyedto the shaft 81 adjacent the gear 98, as shown in Figure 6. Ashereinbefore mentioned and as illustrated diagrammatically in Figure'19, the gears 91 and 90 are of substantially the same size while Thesleeve |08 extends the gears ||2 and IIS, as illustrateddiagrammatically in Figure 20, are of unequal pitch diameter. The gearI9, which is the smaller of the two, is mounted concentrically upon thesleeve ||4 and is therefore eccentric to the shaft 81 as indicated inFigures 6 and 20.

It will now be evident that when the crank pin |00 is adjusted relativeto the shaft 96 to obtain the maximum degree of travel of the crank pinextension |00' about the axis of the shaft 96, as shown in Figure 6, anypoint on the lens, as the center thereof, will be moved a maximumdistance over the grinding surface of the lap 28 as the crank pin 00revolves with the shaft 96 during the rotation of said shaft as producedby the gears H3 and ||2.

It will also be obvious that inasmuch as the eccentric sleeve 95 isbeing continuously rotated at the same rate of speed as the shaft 81,the shaft 96, which is eccentrically mounted in said sleeve, will berevolved about the longitudinal center or axis of rotation of the sleeveat the same rate of speed that the shaft 81 is operated, while the speedof rotation of the shaft 96 about its own axis will be slightly slowerthan the speed of rotation of the sleeve 95 and shaft 81.

It therefore follows that the distance between the axis of the crank pinextension |00' and the axis of rotation of sleeve 95 changing during-the operation of the machine and, therefore, the effective throw of thecrank are constantly pin will be constantly varying and causing the tbeam 5| and each lens driving element 3| to' move through graduallyvarying distances within certain limits. In other words, each drivingelement 3| willmove between the positions 0btained by the maximum degreeof throw produced by the combined action of the crank pin |00, shaft 96and sleeve 95 and the minimum degree of throw produced by the combinedaction of these members.

To explain more explicitly, in Figures 19 to 22 inclusive of thedrawings, circles 91 and 98 represent the gears 91 and 98 and circles||2 and ||3 represent the corresponding gears. The lines A-A and B-Brepresent the axis of rotation of eccentric Ysleeve 95 and shaft 81respectively. These axes, it will be observed, are in xed relation witheach other and lines C-C and-D-D representing the axes of shaft 96 andeccentric sleeve ||4 which are mounted eccentrically to and adapted tobe revolved around the xed axes A-A and B-B respectively. Ashereinbefore stated, Figure 19 illustrates the shaft 81 and eccentricsleeve 95 with the gears 98 and 91 mounted thereon in cooperativerelation with each other. Figure 20 illustrates the shaft 81 and shaft98 and the gears H3 and ||2 associated therewith mounted in cooperativerelation with each other. The teeth of the gears ||2 and ||3 engagingeach other are illustrated by the line a-a, while the side of the shaft96 adjacent the line a-a is represented by the lineb. Figures 21 and 22are each ures 19,and 20.

It will now be readily understood that during a revolution of the shaft81 the eccentric sleeve 95 will operate through a complete revolutiondue to the gears 98 and 91 being of the same pitch diameter.Furthermore, it will be observed that inasmuch as the eccentric sleeve||4 `is keyed to the shaft 81 and gear ||9 is keyed to the sleeve ||4,the gear ||3 will rotate one complete revolution during each revolutionof the shaft 81. The gear H2, however, will be rotated slightly acombination of Fig-- less than a revolution during each revolution ofthe shaft 81 and gear 'H3 inasmuch as the gear ||3 is of smaller pitchvdiameter than the gear ||2. It therefore follows that during eachrotation of the shaft 81 the shaft 88 will be rotated slightly less thanone complete revolution.

In other words, let it be considered that gears 98 and' 31 are eachprovided with twenty-four teeth, that gear ||3 is provided withtwentythree teeth andgear 2 is provided with twentyve teeth, and alsothat the eccentric sleeves 95 and ||4 are arranged so that the axes C-Cand D-D of the shaft 08 and gear ||3 are at one and the same side of theaxes A--A and B-B respectively of eccentric sleeve 95 and shaft 81, asindicated in Figure 21. It will now be obvious that during one-halfrevolution of the shaft 81 and gears 98 and 3 connected therewith fromthe position shown in Figure 21 to the posiytion shown in Figure 22, theeccentric sleeve 95 will be driven one-half revolution while the shaft$6 will be driven slightly less than one-half revolution or to positionb and, therefore, the crank pin will be rotated slightly less thanonehalf revolution. It `therefore follows that the throw of the crankpin |00 will be slightly less than the maximum, which will produce acorresponding shortening in the stroke of reciprocation of theiioating'beam 5| connected to said crank pin by the connecting rod |03.This shortening in the length of succeeding strokes of the iioating beamwill continue during the rotation of the shafts 81 and 96 until theminimum length stroke has beenv reduced, and then these strokes willgradually increase in length until the maximum length stroke is again4reached. V

During continued rotation of the shafts 81 and 96 the axes ofrotation/of gears ||3 and ||2 will be constantly varied with respect toeach other in synchronism with the operation of said gears due totherotation of the eccentric sleeve 95 at the same rate of speed as theshaft 81 for maintaining the gears ||3 and ||2 in constant mesh witheach other, as illustrated in Figures 2l and 22.

The setting of the crank pin |00 to a maximum degree of movement of thelens driving element 29 longitudinally of the grinding surface of thelap is utilized with a lens having a substantially flat surface or onein which the curve of the surface being ground has a relatively longradius. When the surface of the lens being ground has a relatively shortradius, the crank pin |00 is adjusted relative to the end of the shaft96 to bring the axis of the extension |00 thereof into relatively closerelation with the axis of the shaft 06. When the crank pin |00 is thusadjusted to obtain the minimum degree of action produced by the crankpin, the lens driving element 3| will obviously have a much less degreeof movement than with the previously described adjustment ofthe crankpin.

It will be observed, however, that owing to the particular drivingconnection shown between the drive shaft 6 and the crank pin |00 thelens driving element will not only be caused to travel throughcontinuously changing paths or iields of action, but the ends ofsucceeding strokes thereof are continuously changing positions whichreduces to a minimum the liability of scoring or otherwise injuring thelens, as. the lens is moved longitudinally of the base curve of the lap28, by any errors or imperfections in the grinding surface of the lap.This is due not only to ,the positive action of thetransmissionmechanism 88 above described, but also to the more or less indefiniteaction of the belt 85 connecting the shaft 6 with the transmissionmechanisn 88 due to the creeping action of said belt with respect tothepulleys 84 and 86.

'Transverse or cross recprocative movement The mechanism producingreciprocative movement of the beam 5| at substantially right angles tothe reciprocative movement thereof produced by the driving mechanism 88abote described for reciprocating the lens driving element 3| throughthe cross strokes, that is to say, in strokes substantially parallelwiththe cylinder axis of the lens is shown more particularly in Figures2, 3, 7, 8, and 9. This construction comprises an eccentric collar ||6which is secured to the inner end of the drive shaft 6 adjacent thebearing members 1'. In this collar 'H6 isadjustably mounted an eccentriccrank pin ||1. 'I'he pin ||1 issecured in the adjusted position 'by ascrew ||8 which extends through an elongated slot ||9 formed in thecollar |16 and screw-threaded into the pin ||1 in the same mannerv asthe screw |0| shown in Figure 18 for the crank pin |00. The crank pin||1 is provided with an extension H1 arranged in eccentric substantiallyparallel-relation with the axis of the crankv pin. Mounted on theextension H1' is a bearing which is also mounted in one,

end of a connecting rod |2| extending downwardly from the crank pin. Theconnecting rod has the lower end thereof provided with a bearing l|20'in which is mounted one portion of an eccentric crank pin |22 which ismaintained in xed spaced relationto crank pin extension H1' by saidconnecting' rod, as shown in Figure 3.v The crank pin |22 is providedwith anextension |22 arranged in eccentric substantially parallelrelation to the axis of the crank pin |22. Upon extension |22' ismounted a bearing |20" which is also mounted in one end of a drive link|23 having the opposite end thereof secured, as by a pin |24 or othersuitable means, to one end of a tubular sleeve |25. The sleeve |25 issecured by a screw |26 in the boss 12' connected with the rock frame 12to extend outwardly from one end of the frame in a plane over theadjacent stub shaft 13, as illustrated in Figure 8.

It will now be observed that when the crank pin ||1 is secured in thecollar HS, rotation of the shaft 5 will produce a vertical reciprocatingmovement of the connecting rod |21 and the rear end'of the drive link|23 which in turnwill produce a corresponding rocking or oscillatingmovement of the frame 12. This rocking of the frame 12k will produce asimilar rocking or reciprocating movement of the floating beam 5|through the mediumI of the supporting rock 'frames 10, which in turnvproduces reciprocative movement of the lens driving elements 3|connested therewith in a direction substantially parallel with the minoror cylinder axis of the lap 28.

In order that --the transverse or cross strokes of the lens drivingelements 3| thus produced may be varied so that a variation in the pointof reversal of the lens driving elements, and therefore of the lenscarried thereby, at the ends of the strokes maybe produced, I haveprovided a simple mechanism for" rotating the eccentric crank pin |22about the axis of bearing |20 mounted in the lower end of connecting rod|2|.

This mechanism 'comprises a drive pulley |28 secured, as shown in Figure3, to the outer end of the extension of the crank pin I 1. The pulley|28 may be secured to said extension in any suitable manner so as torotate in unisonn therewith. The pulley |28 is connected by a belt |29to a similar pulley |30 secured to the crank pin |22, so that saidpulley and crank pin will rotate in unison. Pulleys |28 and |30 are thusmaintained in fixed spaced relation with respect to each other and thepulley |30, as shown, is of slightly greater diameter than 'the pulley|28 so that the crank pin |22 will be rotated at a slightly slower rateof speed than the crank pin ||1.

It will now be seen that this continuous rotation of the crank pin |22will vary the distance between the axis of the extension |22' of saidpin and the axis of rotation of the crank pin ||1, that is, of shaft 6,and will therefore vary the effective length of the connecting rod |2|.It therefore follows that a continual change will be produced in thecross stroke of each lens driving element dueA to a continual change inthe lengths of succeeding strokes of the beam and that the movement ofthe lens across the grinding surface of the lap will be correspondinglyaffected thereby. It will be seen from the foregoing description thatthe two reciprocative movements when combined with the two break-upmovements will be synchronous and simultaneous, resulting in the travelof the lens across the face of the lapin serpentine paths and also inthe gradual and continuous changing of these paths during successivelengthwise and transverse `strokes of the lens driving elements, asclearly illustrated in Figures 28, 29, 30 and 31.

It will now be noted that inasmuch as all the co-acting relativelymovable members of the mechanism mounted within the frame are supportedby bearings of the roller bearing type arranged in suitable housings toprotect them from dust and other foreign material, the machine may besuccessfully operated without the use of an oil pump or aliquidlubricant being supplied to said bearings.

PTeSSuTe means Each lens is yieldingly held against the surface of a lap28 partially by the Weight of the front end of the lens driving element3| and saddle 55 and partly by means of an upright pressure rod |32 anda coil spring |33 mounted in said rod. The rod |32 is composed of twotelescoping tubular sections |32 and |32 and the spring. |33 is mountedwithin said sections between opposite ends thereof. The inner section,as |32", has the lower end thereof provided with a ball |34 which isadapted to releasably engage a seat |35 connected with'the spindle 46and which is formed by extending a portion of the outer end of saidspindle, as shown in Figure 14. The upper end of the outer tubularsection |32 is provided with a ball |34 which is seated in a socket |36provided in the lower end of a stem |31 of a pressure gauge |38. Theball |34' is preferably secured in the socket |36 so that the pressurerod 32 will be secured to the pressure gauge |38. The pressure gaugeis'mounted upon an outwardly extending arm |39 formed integral with asupporting slide or bracket |40 mounted on a standard |4| secured to ormade integral with the upper section 3 of the frame The stem |31 isyieldingly urged downwardly to its lowermost position by a spring |42coiled about said stem between the lower end thereof and a nut |43engaging the threaded sleeve connected to the gauge |38 and whichservestfo clamp the gauge to the arm |39.

The bracket 40 is a tubular member which is mounted for vertical`reclprocative movement upon the standard 4|. The bracket |40 ismaintained with the arm |39 in predetermined aligned relation with thecorresponding spindle 46 of the respective lens driving element 3| bymeans of a screw |45 screw-threaded in the side of the bracket and whichhas the inner end thereof slidably received in a vertically disposedslot |46 provided in a guide post or a stud |41 secured to' the upperend of the standard |4|, as shown in Figure 14.

The vertical movement of the slide or bracket |40, and therefore thegauge |38, is controlled by a lever |50 which is rotatably mountedintermediate the ends upon a pin |5| secured to the upper end of thebracket |40. 'I'he upper or rear end of the lever |50 extends a shortdistance beyond the pin |5| and is pivotally connected, as at |52, toone end of a link |53 which has the other end pivotally connected at |54to the upper section 3 of the frame as shown in Figure13. Mounted uponthe pin |5| intermediate the lever |50 and bracket |40 is a ratchetwheel |55 which is secured by pins |56 to the bracket 40 to maintainsaid ratchet wheel against rotation. A ratchet pawl |51 is pivotallyconnected at |58 to the lever |50 at the lower or forward side of thepin |5|. 'I'he pawl |51 is provided with a finger piece |51' whichextends outwardly therefrom in close cooperative relation with the outerend of the lever |50 which is curved, as shown in Figure 13, to providea finger piece |50. The pawl |51 is urged into engagement with theratchet wheel by a spring |59 mounted in the lever |50 and whichisadapted to engage the finger piece |51', as shown in Figure 16. 'I'heteeth, as |55', and the ratchet wheel |55 are ar ranged in one sideportion thereof only so as to be engaged by the pawl |51 when pressureis being exerted by the spring |33 upon the lens driving element,'or, inother words, when the bracket |40 is inv a lowered position. When theaction of the spring |33 upon the spindle 46 is to be discontinued, thebracket 40 and rod |32 are raised to an upper inoperative position byswinging the lever |50 about the pin |5| until the pivot |52 has passeddownwardly and'through the -straight line extending between the pivot|5| and the pivot |54, whereupon the weight of the bracket |40, gauge|38 and rod |32V will counter-balance the action of the upper or innerend of the lever |50 and link 53 for releasably4 securing said bracket,gauge and rod in the upper position.

'I'he rod |32 is maintained in cooperative engagement with the spindle46 during the upward movement of the bracket |40 by a rod |60 which hasthe upper end portion extending through an aperture |39 formed in thearm |39 intermediate the bracket |40 and the gauge |38. 'I'he lower endof the rod |60 is secured in a ring |6| mounted upon the boss or hubportion 54' of the bracket 54 as shown in Figures 2 and 14. This ring|6| is removably mounted on the hub so that the bracket 54 may readilybe removed from the spindle 46 and from said ring during thesubstitution of one bracket 54 for another. 'I'he upper end of the rod|60 is provided with a pair of nuts |62 so related to the ring |6| andarm |39 that prior to the rod 32 being moved out of engagement with theseat |35 as the bracket' |40 is moved upwardly, said nuts will engagethe arm |39 and subsequently cause the outer end of the spindle 46 tomove upwardly in unison with the bracket |40. This upward movement ofthe spindle 46 is permitted by rotation oi' said spindle 6 about theaxes of the stub shafts 50 and 50' associated with the D-frame 48 withwhich said spindle is connected. A y

It will be understood that there is one of these pressure devicesforeach of the lens driving ele- 10 ments, and the operation Yoi each ofthese pressure devices will now be understood to be substantially asfollows: After a lens secured to one .of the saddles 55 has been placedupon a lap 28 the lens driving element 3| will be moved from 1l theupper inoperative position downwardly by the operator swinging the lever|50 about the Vpin |5| to move the bracket |40 downwardly. It

will be obvious that during this downward movement of the bracketthespindle 46 will move in unison with the arm |39 until the downwardmovement of the spindle is limited by the engagement of the pins 58 withthe bearing members-51 provided on the saddle 55. During this downwardmovement of the bracket and spindle there will be no appreciablepressure inserted by the spring |33 upon the spindle. In other words,the pressure gauge |38 will have a zero reading. As soon, however, asthe spindle 46 is maintained against downward movement by the engagementof the pins 58 with the bearings 51 when the saddle is supported by theengagement of the lens with the lap, any further downward movement ofthe arm |39 will tension the spring |33 by decreasing the over-alllength of the rod |32.

85 This pressure tension of the spring |33 will be registered in thegauge |38, so that the operator may readily determine the pressure beingexerted by the spring upon the spindle 46 which will more or lessaccurately indicate the pressure 40 between the lens and the grindingsurface of the lap. When the downward movement of the bracket |40 issufhcient to produce the required tension of the spring, the bracket maybe secured in that position by the engagement of the ratchet pawl |51with the` ratchet wheel |55. When the lens is again to be released fromthe lens driving element, this may be readily accomplished by theoperator using the nger pieces and |51 to move the pawl |51 out ofengagement with the 50 ratchet wheel |55 against the action of thespring |59, after which the lever |50 may be readily moved to itsuppermost position and thus move and maintain the lens driving elementin its uppermost inoperative position. 55 Rouge pump In order that rougemay be applied to the\ grinding surface of the lap during the polishingof` lenses, I have 'provided a simply constructed pump attached to thecatch basin 39. This pump comprises a pump case which is secured to oneend of the catch basin 39 by one or'more `screws |66. This pump case isprovided with a pump chamber |61 in which is rotatably mounted 65 arotary pump |68 which is secured to the lower end of a motor shaft |69as shown in Figures 10 and 12. The shaft |69 extends upwardly from thepump chamber and case |65 through a verti` cally disposed standard |10connected at its 70 lower end to the case |65. The upper end of thestandard is connected with and supports an electric motor |1| connectedwith the opposite or upper end of the shaft |69. The standard |10 is.

provided with suitable bearings |12 in which t shaft |69 is journaled.

'rne intake side erthe pump chamber |61 is connected by an inlet passage|14 provided in 1 the case |65 withv the adjacent end of the interior ofthe catch basin 39-which has the bottom wall 38 thereof inclinedupwardly -from the inlet 5 opening |14 to the opposite end of the catchbasin, as illustrated in Figure 10. The case |65 is also provided withan outlet or discharge passage |15 which has Vthe outer end thereofregistering 'with the interior of the catch basin |39 10 adjacent theouter or front wall thereof, as illustrated in Figure 12. 'Ihe end wallof the catch basin adjacent the pump case |65 is pro- ,vided with anopening |14' registered with the inlet opening |14 in said case and asecond open- 15 ing |15 in registration with'the exhaust passage Adistribution tube |16A is positioned in the catch basin |39 to extendfrom within the opening |15' along the front side wall ofthe catch 20basin and then inwardly along the end 4wall ofA said basin opposite thepump case, as illustrated in Figure 2. The tube |16 has the outer endthereof adjacent the rear wall of the catch basin closed and is providedwith a pair of laterally 25 projecting tubes |11, one for each lap 30.These lateral tubes |11 extend upwardly and inwardly fromrthedistribution tube |16 to a. position adjacent to and slightly above thecorresponding lap 28 for continually supplying said lap and the lens 30surface being ground thereon with rouge. The excess rouge deposited uponthe lens and lap flows downwardly to the inclined wall 38 of the catchbasin and then down said wall to the opening |14 and inlet passage |14back to the pun'ip` 35 Y |68. The distribution tube |16 merely restsupon the bottom wall 38 of the catch basin when the inlet end thereof isinserted in the discharge opening |15' of the catch basin, so that said.tube may be readily removed for the purpose of 40 cleaning or for anyother reason, by simply lifting the tube out of the catch basin. It isobvious that the tube may as readily be placed in operative positionwithin the catch basin by inserting the inlet end thereof in the opening|14 and 45 positioning the laterally disposed opposite end of the tubealong the end of the catch basin opposite the pump.

As hereinbefore stated, the rouge pump |68 and distribution tube |16 areusedto supply 50 rouge to the grinding surface of the laps whenpolishing lenses. When it is desired to use a grinding compound such asemery dust or the like, in grinding a lens, the catch basin 39 togetherwith the pump |68 and motor |1| are re- 55 moved from the supportingframe by the manipulation of the bolts 43 and washers 44 inthe mannerhereinbefore described, and another catch basin of suitable structureand design' for collecting the dust and excess grinding compound 50 maybe secured to the supporting frame by the screws43 and washers 44 in thesame manner in which the catch basin 39 is secured to said frame.

Although I have shown and particularly-dee5 scribed the preferredembodiment of my invention, I do not wish to be limited to the exactconstruction shown, as various changes, both in the form' and relationof the parts thereof, may. readily be made without departing from thel70 spiritof the invention as set forth in the appended claims.

I claim:

1. In a surface grinding and polishing machine having a grinding memberand a work 75 35 to the driven shaft, means operatively connecting.

holding member. operating mechanism for producing relative movement ofsaid members oomprising a rotary drive shaft having an eccentric, aconnecting rod journaled on said eccentric, a driven element journaledon the connecting rod having an eccentric operatively connected with oneof said membersl for producing reciprocative movement thereof, means fortransmitting rotary movement from the drive shaft to the driven elementcomprising a pulley secured to the eccentric of the drive shaft, asecond pulley connected to the driven element to rotate therewith, and aflexible friction belt connecting `said pulleys.

2. In combination, an actuating member mounted for reciprocativemovement in two directions, means for reciprocating the member in one ofsaid directions, and additional means for reciprocating the member in asecmd of said directions comprising a drive element mounted to revolveabout a fixed axis, means including a head Journaled on the driveelement and a connecting rod fixedly secured to said head and to. theactuating member operatively connecting the drive element with theactuating member, said connecting .rod being adapted to flex laterallyduring the reciprocative movement of the actuating member in the rst ofsaid directions.

3. The combination with an actuating member mounted for reciprocativemovement, of a drive mechanism for producing reciprocation of theactuating member through strokes of varying lengths comprising a drivenshaft mounted to rotate about a fixed axis, a second shaft having aneccentric and mounted in spaced relation the eccentric with theactuating member, means including a pair -of gears one secured to thesecond shaft and the other secured to' the driven shaft and meshing withsaid rst mentioned gear operatively connecting the second' shaft withthe driven shaft whereby the second shaft will be rotated by the drivenshaft at a different rate of speed than that of said driven shaft,and'separate means connecting said shafts whereby the second shaft willbe revolved by the driven shaft about an axis arranged in eccentricrelation with the axes of rotation of both of said shafts'including arotatable sleeve rotatably supporting 'said second shaft in eccentricrelation with the axis of rotation of said sleeve, and a second pair ofintermeshing gears secured to said sleeve and driven shaft respectively.

4. The combination with a rotary drive shaft and anV actuating membermounted for reciprocative movement, of two drive mechanisms operativelyconnecting the shaft with the actuating member for producing tworeciprocative movements thereof operating in directions at substantiallyright' angles to each other and through strokes of varying lengths, oneof said drive mechanisms comprising a driven shaft mounted to rotateabout a fixed axis, a second shaft having an eccentric and mounted inspaced relation to the driven shaft, means operatively connecting theeccentric with the actuating member, means operatively connecting thesecond shaft with the driven shaft whereby the second shaft will berotated by the driven shaft at a different rate of speed than .that ofthe driven shaft, separate means connecting said shafts whereby thesecond shaft will be revolved by the driven shaft about an axis arrangedin eccentric relation with the axes of rotation of both of said shafts,and means including a belt operatively connecting the driven shaft withsaid drive shaft independently of the other one of said drivemechanisms.

5. The combination with an actuating member mounted for reciprocativemovement, of a drive mechanism for producing reciprocation ofA erativelyconnecting said shaft eccentric with the actuating member for producingreciprocation of said member, and means including two pairs ofintermeshing gears rotatably connecting the driven shaft with the sleeveand with said second shaft, one pair of said gears being secured to thedriven shaft and to the second shaft respectively. the gear on saiddriven shaft being eccentrically mounted with respect thereto, and theother pair of said gears being secured to the driven shaft and to theeccentric sleeverrespectively, two of the gears of said pairs of gearsbeing of different pitch diameter than the other two gears so that saidsecond shaft and sleeve will be simultaneously rotated at differentspeeds.

6. The combination ,with an actuating member mounted for reciprocativemovement, of a drive mechanism for producing reciprocation of saidmember through strokes of varying lengths com-' prising a driven shaftmounted to rotate about a nxed axis. an eccentric sleeve mounted torotate about a xed axis arranged in predetermined spaced relation tosaid axis of rotation of said' tuating member for producingreciprocative movement thereof in directions at substantially rightangles to the direction of the first mentioned reciprocating movement,and means in- -cluding a belt operatively connecting the ldrive shaftwith said driven shaft.

7. In a surface grinding and polishing machine having a grinding elementand a work holding element arranged in cooperative relation with each'other, operating mechanism for producing relative movement of saidelements comprising a rock frame mounted to swing about a fixed axis, asupporting floating member mounted in a plane above the rock frame,means including hollow frame members pivotally connecting the floatingmember tothe rock frame whereby said floating member may be reciprocatedin a direction extending substantially parallel with the axis 4ofrotation of the rock frame, means connected with the rock frame forproducing swinging movement thereof and` the floating member about saidaxis. means 'operatively connecting the floating member with one of saidelements, means for producing reciprocative movement of the floatingmember independently of said swinging movement thereof including aflexible substantially straight connecting rod extending through thehollow frame intermediate the rock frame and said floating member andfixedly connected with the floating member, and means connected with theconnecting rod for producing reciprocative movement thereof in adirection substantially parallel with said axis of the rock frame. y

8. In a surface grinding and polishing machine having a grinding memberand a work holding member, in combination, operating mechanism forproducing reciprocative movement of oneof said members with respect tothe other member including a supporting floating element pivotallymounted to reciprocate in two directions substantially at right anglesto each other, a D-frame arranged in substantially parallel relationwith the floating element and -pivotally connected to said element incoaxial relation therewith and to rotate about an axis extendingsubstantially parallel With'one of said directions of reciprocation ofsaid iioating element, a spindle journaled inv said D-frame with thelongitudinal axis thereof intersecting said axis of rotation of saidD-frame substantially normal thereto, a saddle connected with said oneof the members to extend to opposite sides thereof, means including aforked bracket connected with the spindle, and

of rotation pivotal bearing means associated with the bracket and saddlearranged substantially in a plane extending diametrically through saidspindle for operatively connecting the spindle with the ends of saidsaddle.

9. A structure as in claim 8 having means operatively engaging thespindle for maintaining the work carried by the work. holding member inpressure engagement with the grinding member.

10. In a surface grinding and polishingma.- chine having a grindingmember and a work holding member mounted in cooperative rela.

y tion with each other, means'including a driving element operatively.connected with one of said members for producing relative movement of ithe members with respect to each other, and means for maintaining thework carried by the work holding member in pressure engagement with thesurface of the grinding member including a. spring, a support for saidspring having engagement with the driving -element, manually operatedmeans connected with said'drivi'ng element and spring support for movingthe same and the member connected therewith toward and from the othermember, means connected with the manually operated means and springsupport for tensioning the spring carried by said support after the Workis brought into engagement with the grinding member, and a pressuregauge carried by the manually operated means and connected with thespring for indicating the amount o f pressure between. the work and thegrinding member.` A

11. A structure as in claim 10 having means including a ratchet wheeland p'awl associated with the manually operated means and springbermounted on said frame, a work holding member arranged in cooperativerelation with said grinding member, and operating means including adriving element connected with the work holding member for producingmovement thereof with respect to the grinding member to effect grindingof the surface of the Work carried by said work holding member, thecombination with said frame and operating means of means for maintainingthe work in predetermined pressure y engagement with the grinding membercomprising a pressure rod composed of telescoping sections, havingengagement at one end with the driving element, means including asupporting -member connectedwith the frame for movement toward and fromthe driving element and supportably engaging said pressure rod,additional means connected with the driving element and engaging thesupporting member at a predetermined position of said member for causingthe driving element to move toward and from the grinding member during aportion of the movement of the supporting element, and means including aspring mounted in the pressure rod rendered effective after the workcarried by the work holding member is brought into engagement with thegrinding member for producing a predetermined pressure between said workand grinding members.

13. In a surface grinding and polishing machine having a grinding memberand aworx supporting member arranged in cooperative re lation with eachother, a catch basin mounted' beneath said members and provided 'with apair of fluid passages in communication with the interior thereof, apump secured to the-catch basin with the inlet port in communicationwith one of said fluid passages and the exhaust port thereof incommunication with the other one of said ud passages, and a conduitremovably connected with the catch basin in communication with the lastmentioned fluid passage adapted to supply rouge between the work carriedby the Work supporting member and the grinding member.

14. In a precision surface grinding and polishing machine of thecharacter described wherein a grinding member and a work holding memberkare mounted in cooperative relation with each tric, said connecting rodhaving a bearing member mounted in spaced relation to the shafteccentric, a rotary driven element rotatably mounted in said bearingmember lto be carried by the connectingrod, means for transmittingrotary motion from the drive shaft to said driven element including apulley secured to the-eccentric of the drive shaft, a second pulleysecured to the driven element in coaxial relation with the bearingmember, a flexible belt connecting said pulleys, anda second connectingrod rotatably connected with the driven element in eccentric relation tosaid bearing member operatively connecting the driven element with oneof said members.

i' WILLIAM A. LOCKHART.

